Multiple station hydraulic metal working machine



June 23, 1959 R. K. SEDGWICK 1 MULTIPLE STATION HYDRAULIC METAL WORKING MACHINE:

I 9 Sheets-Sheet 1 I Filed June 17. 1953 "June 23, 1959 R. K. SEDGWICK I MULTIPLE STATION HYDRAULIC METAL WORKING MACHINE- 9 Sheets-Sheet 2 Filed June 17. 1953 INVENTOR.

File d June 17. 1953 MULTIPLE STATION HYDRAULIC METAL WORKING MACHINE 9 Sheets-Sheet a June 23, 1959 v K. QSEDGLNICK i811 150 INVENTOR.

32 fig Q' ded gwicz 1128 w -o 12 1 9 June 23, 1959 R ..K.SEDGWICK 2,891,431

MULTIPLE STATION HYDRAULIC METAL WORKING MACHINE Filed June 17, 1953 9 Sheets-Sheet 4 INVENTOR.

June 23, 1959 Filed June 1'7. 1953 R. K. ISEDGWICIK MULTIPLE smxon HYDRAULIC METAL woaxms MACHINE 9 Sheets-Sheet 5 IN V EN TOR.

R. K. SEDGWICK June 23, 1959 MULTIPLE STATION HYDRAULIC METAL WORKING MACHINE 9 Sheets-Sheet 6 Filed June 17, 1953 figmi eg /232% June 23, 1959 R. K. SEDGWICK I 2,891,431

MULTIPLE sm'rou HYDRAULIC METAL woaxmc; MACHINE 9 Sheets-Sheet 7 Filed June 17, 1953 June 23, 1959 R. K. SEDGWICK 2,891,431

MULTIPLE STATION HYDRAULIC METAL WORKING MACHINE Filed June 1'7, 1955 v 9 Sheets-Sheet 8 Hm w Nmfi .QN

Em am 9. .25 on J 8 m Qk NE I V in wl w a v $5 q Em m6 e um 39%. q 4 ME 2 i 3W mm N .N W'- DQOW-NQA TNMA m mum .m FL "ll 3% MN Own 3 o mw June 23, 1959 Filed June 17. 1953 R. K. SEDGWICK MULTIPLE STATION HYDRAULIC METAL WORKING MACHINE 9 .Shee ts-Sheet 9 email) TURRET UP (501.;J)

INDEX 'TURRET (501" H) United States Patent MULTIPLE STATION HYDRAULIC METAL WORKING MACHINE Robert K. Sedgwick, Cincinnati, Ohio, can Steel Foundries, Chicago, Ill., New Jersey assignor to Ameria corporation of My invention relates to a hydraulically operated metal working machine and to electrical and hydraulic control circuits therefor. More particularly the invention comprehends a fully automatic progressively staged hydraulically operated metal working machine.

In the metal forming art today, and more particularly that type of metal forming known as upsetting, the work is most frequently done on mechanical machines. The use of mechanical upsetters has presented inherent problems both from the standpoint of the operating machine itself and from the standpoint of the product produced. In the case of the machine, it is well known that the mechanical actions employed to work the metal produce variable forces which at certain points in the work stroke are indeterminable and which theoretically may approach infinity. Because the quantum of available force at particular points of the stroke is unknown and because of the close tolerance requirements of work of this nature, good design demands extreme rigidity in the machine construction. To obtain the required rigidity, mechanical machines must be made enormously heavy, whereby the unknown forces may be safely accommodated. In the case of the piece part, the fact that the working forces vary over the stroke of the machine frequently adds such difliculty to the forming operation that poor quality piece parts result.

Considering the above mentioned problems, I have provided a hydraulic machine which will accomplish the same work at substantially the came or better production rates and at substantially decreased original machine cost and produced product cost.

In the hydraulic machine hereinafter described, the exact working forces can accurately be determined through all positions of the work stroke. Because such forces are determinable, component machine parts can be designed to reasonably accommodate the working forces so as to afiord the required maximum rigidity without excessively heavy structure. Needless to say, this results in enormous saving in machine weight because unknown forces do not have to be accounted for. In addition, the determinable working forces are controllable and constant for a given design, hence my machine can deliver correct working pressures to accomplish a given task. The obvious result is the production of more consistently satisfactory piece parts with the consequent reduction of scrap loss.

Accordingly, it is a general object of my invention to provide a hydraulically operated metal working machine of lighter construction and lower cost than those presently used in the art.

Another object of my invention is to provide a hydraulically operated machine which will deliver constant determinable working pressure to accomplish a given task.

A further object of my invention is to provide a hydraulically operated machine capable of doing that type of metal forming known in the art as upsetting.

A more specific object of my invention is to provide Patented June 23, I959 2 a hydraulically operated progressively staged metal forming machine.

Another specific object of my invention is to provide a hydraulically operated progressively staged metal forming machine wherein the piece parts are rotatively fed to each stage or working position.

Another specific object of my invention is to provide a hydraulically operated progressively staged metal forming machine wherein provision is made for heating the piece part and working same while hot.

Still a more specific object of my invention is to provide a hydraulically operated progressively staged machine for forming heated metal wherein provision is made for piece part reheating stations, if desired.

A further specific object of my invention is to provide a hydraulically operated rotatively feeding progressively staged metal working machine wherein the machine operation is completely automatic.

Still another specific object of my invention is to provide a hydraulically operated progressively staged metal forming machine wherein the individual operating mechanisms may be independently operated.

Still another specific object of my invention is to provide electrical and hydraulic control circuits for a machine of the type described.

Yet another specific object of my invention is to provide a progressively staged hydraulically operated metal working machine wherein provision is made for the addition or reduction of the number of operating stages thereby adding flexibility to the machine.

My invention comprehends a rotatable turret, operative dies disposed adjacent the turret, and clamps operative to separate said dies. Adjacent each die a forging station is positioned operable to urge an associated punch into engagement with the related die, whereby a piece part undergoes a desired formation. In operation of my machine, heated tubes are inserted into the turret, the clamps are raised and the turret progressively indexes said tubes into the associated dies. After indexing, the clamps again descend reengaging the separable die halves, whereupon the forging rams are actuated causing the metal forming operations at the various stations. As the cycle is repeated, a completed piece part is ejected from the machine and an unformed piece part is inserted in the machine with each cycle operation.

The above and other objects of my invention will become apparent in the course of the following discussion and from an examination of the drawings, wherein:

Figure l is a general side elevational layout of a machine embodying my invention;

Figure 2 is a top plan view of the machine table approximately along line 22 of Figure 1 Figure 2A is a sectional view taken along line 2A, 2A of Figure 2;

Figure 3 is a fragmentary support assemblies;

Figure 4 is a fragmentary sectional view taken along line 4-4 of Figure 3;

Figure 5 is a fragmentary sectional line 55 of Figure 3;

Figure 6 is a fragmentary sectional side elevational view of a typical forging station die and cylinder assembly;

Figure 7 is a fragmentary sectional side elevational view completing the forging station die and cylinder assembly of Figure 6;

Figure 8 is a view taken along line 8-8 of Figure 7;

Figure 9 is a sectional view taken along line 9-9 of Figure 8;

Figure 10 is a fragmentary detail view of the turret indexing mechanism shown in Figure 2;

Figure 11 is a fragmentary side elevational view of taken top view of the upper clamp view taken along the ejector mechanism taken along line 11-11 of Figure 2;

Figure 11-A is a fragmentary sectional view taken along line 11--A, 11--A of Figure 11;

Figure 12 is a fragmentary side elevational detail view of the loading mechanism;

Figure 12-A is an end elevational view of the loading mechanism of Figure 12 taken from the left and with the hydraulic cylinder removed;

Figure 13 is a schematic hydraulic circuit layout of the entire machine, and

Figure 14 is a schematic electrical control wiring diagram.

Describing the invention in detail and directing attention to Figure 1, it will be seen that my novel hydraulic machine comprises a foundation 2 upon which rests a base 4. Adjacent one end of the base 4 a pivot column 6 is secured to the base extending thereabove to interconnect the base with the turret and frame assemblies 8 and 10, respectively.

As Will be seen from Figure 1, the turret assembly 8 comprises a rotatable turret 12 having a plurality of radially directed piece part holding holes 14, said turret being rotatable, preferably in a counterclockwise direction about the pivot column 6. The frame assembly comprises frame arms 16 and 18 having adjacent ends pivoted to the upper end of the pivot column 6 and having opposite ends column connected to the respective segments of the base 4, as hereinafter described.

The frame arms 16 and 18 carry the die plates 29, which are vertically slidable on the related column connections, one of which is indicated at 22. Said die plates carry the upper halves of the forming die 24. The frame arms 16 and 18 also carry hydraulically actuated clamps or clamping ram assemblies, one of which is indicated at 25, said clamps being operative to raise and lower the associated die plates and the upper half of the associated forming die 24.

A plurality of forging ram stations 26 are disposed radially on the table 4 about the turret 12. Each station comprises a hydraulically operated power ram 28 connected to a reciprocal punch mounting device 29, which in turn is gibbed to the table in such a manner that an associated punch will complementally engage the die 24.

It will also be noted that the hydraulic motors 30, 30 are mounted on the pivot column 6 and connected to the turret in such a manner that the turret may be raised or lowered in response to the action of said motors.

A hydraulic system control panel 31, consisting of a plurality of controlling valves and electrical solenoids (not shown), is positioned at a point adjacent the machine, said panel controlling the various hydraulic systems, as hereinafter described.

Directing attention now to Figure 2, it will be seen that the work table 4 comprises two segments 32 and 34. Each segment in the preferred embodiment mounts a plurality of independent forging ram-die assembly stations, segment 32 mounting three stations and segment 34 mounting two stations. Intermediate the segments 32 and 34, a space 36 is available, in the preferred embodiment, said space being useable as desired, for example, by conventional piece part reheating equipment if it be comes necessary to reheat said parts before completing the final working stages. It will also be noted that the segments 32 and 34 pivot independently about the column 6, hence the space 36 may be eliminated or made larger as job requirements demand.

The various forging stations or ram-die assemblies 26 are similar in construction and operation. It will be noted, however, that the individual stations may easily be designed to exert different working pressures depending upon the requirement of the particular state of operation. In this connection, it will be noted that the dies 24 are shown in Figure 2 with their upper die sec- 4 tions removed and an illustrative completed piece part is shown located within each die.

Each forging ram station consists of an operating cylinder 28 and a connected reciprocal punch mounting de vice 29. As noted above, each device 29 is slidably guided by the associated ways 40 and gibs 42. A lost motion limit switch actuating arm 44 is slidably mounted adjacent each forging ram on the brackets 46. Limit switches LS1 and LS8 are mounted on the table adjacent each arm 44 of each station. Adjustable limit switch actuating collars 48 and St on each arm 44 are engageable with the associated switches LS1 and LS8. Adjacent the inboard end of each arm 44 actuating collars 52 and 54 are adjustably secured to said arm. Intermediate the collars 52 and 54 and loosely sleeved over the arm 44 is the lever 56 which is fixedly secured to the reciprocal punch mounting device 29. It will thus be understood that as the device 29 approaches the extreme advance and return stroke positions, the lever 56 engages one of the collars 52 and 54, which in turn causes the arm 44 to move whereby the limit switches LS1 and LS8 are tripped. A more complete description of the action of the arm 44 and limit switches is hereinafter included.

High pressure ram advance line 60 is manifolded outwardly of the table 44 and connected to the advance chamber of each ram 28. A high pressure ram return line 62 is also manifolded outboardly of the table and connected via lines 64 to the return chamber of each ram cylinder 28.

Intermediate each die 24 and the turret 12 is a limit switch LS9. Each limit switch LS9 is electrically interlocked with a control valve 66, as will hereinafter be explained in connection with the electrical control circuit. Suffice it now to say that if a tube fails to appear in position in each die 24, the related switch LS9 is closed, which results in actuating fluid from a pneumatic manifold 68 being directed to the diaphragm valve 70. Actuation of the diaphragm valve 70 closes the high pressure line to the associated ram station advance chamber, thus preventing the particular station from functioning and preventing unnecessary punch and die damage due to closure of said punch and die Without a piece part being in position. It will be noted that each ram station has an independent interlocked switch LS9 and diaphragm valve 70, thus the above described action may occur at one station without affecting the operation of the other stations or the operation of the over-all machine. This action obviously occurs when machine operation is first started and continues until the turret is completely filled with piece parts.

Attention is now directed to the rotatable turret 12 and to the plurality of radially extended holes 14 therein. Each hole 14 complementally receives a frictionally operated tube holding device 74, each device 74 being held in place within the turret 12 by an associated lock screw 76.

Figure 2-A illustrates in detail one of the tube holding devices 74. It will be seen that the device 74 comprises a hollow cylinder 78 complementally received by the hole 72 of the turret 12 and having a flange 80 abutting the radially outer periphery of the turret. The=flange 80 has formed therein a plurality of slots 82 extending radially of the axis of the cylinder 78. The slots82 are desirably of equal angular spacing, for example, three slots disposed at and have positioned therein reciprocal locking tongues 84. Each tongue 84 has a spring recess 86 which receives and seats one end of a tongue actuating spring 88. The opposite end of the spring 88 reacts against the flange 88 by compressively abutting the flange fixed dowel pin 96 A retainer plate 92 is bolted to the flange 88 whereby the tongues 84 are movably maintained in position. The action of the spring 88 is to urge the related tongue 84 inwardlytoward the longitudinal axis of the cylinder 78. An abutment pin 93 a site ends thereof as at 122 limits the inward movement of each tongue by engagement with the peripheral surface of the retainer plate 92.

It will be noted that each tongue 84 is tapered as at 94 toward the open end of the cylinder 78. When a piece part is forced into the cylinder 78 it strikes the tapers 94 of the associated tongues urging same camlike outwardly against the increasing compression of the springs 88. The piece part is moved within the cylinder 78 until it strikesa stopping abutment, herein in the form of a set screw 96, at a point adjacent the rear of the cylinder 78. The piece part is now in position in the turret and frictionally held in said position under the action of the locking tongues 84.

Again considering Figure 2, it will be seen that the table segment 32 supports a turret loading or delivering mechanism 100 which will be discussed in detail when consideration is given to Figure 12. It should be noted, however, that the loading mechanism has an operating cylinder 102 which is air operated being connected by the line 103 to the air manifold 68. -Valves 104 and 106, respectively, control the fluid flow to the cylinder advance and return chambers.

Rigidly secured to the base segment 34 is the plate 108 which serves as a mounting for the turret stripping or ejector unit 110 which will be discussed when consideration is given to Figure 11.

Also mounted on the table segment 34 is the turret indexing mechanism 112, the detail operation of which will be considered in conjunction with Figure 10.

Figures 3, 4 and show various fragmentary views of the turret and upper clamp arm assembly. In the plan view of Figure 3, it will be seen that the arms 16 and 18 are pivotally connected to the column 6, the arm 18 also being connected to the table segment 34 by the column connection 22 (Figure 2) and the arm 16 being connected to the table segment 32 by column connections 114 and 115 (Figure 2). Figure 3 also illustrates the angular relation between the frame arms 16 and 18, said angular relation being dependent upon and equal to the angular relation of the table segments 32 and 34.

Referring to Figure 4, it will be noted that turret 12 presents a central bore 120 which is counterbored at oppoand 124, respectively, to receive the outer bearing races of the bearings 126 and 128. A cylindrical insert 130 is sleeved over the column 6 and disposed within the bore 120 whereat it supports the inner races of the bearings 126 and 128. A cylindrical spacer 132 is sleeved over the insert 130 and serves to properly space said inner races of said bearings. The lower end of the insert 130 threadably receives the retaining collar 134 which serves to interlock the insert with the turret.

Insert 130 is flanged as at 136, 136, said flanges having connected thereto the lower ends of adjustable piston rods 138, 138. Mounted on the underside of arm 16 and at opposite sides of the column 6 are the hydraulic motors 30, 30. The piston rods 138 are connected internally of the respective motors to reciprocal pistons (not shown). Actuation of the motors 30 raises the turret assembly 12 a predetermined distance, the purpose of which will be hereinafter explained.

The turret 12 also comprises the vertically spaced radially extended flanges 142 and 144, the upper flange 142 serving as a mounting for the tube holding devices 74 and the lower flange 144 serving as a mounting for a ring gear 146, which is securely bolted thereto as at 148.

Intermediate the flanges 142 and the ring gear 146, a rack 150 is disposed in such a manner that the rack will engage the ring gear during the before mentioned raising of the turret. It will also be noted that the ring gear has a plurality of vertical locking holes disposed arcuately within the gear, one of said locking holes beingillustrated at 152 receiving a locking pin 154, which is securely attached to the table 4. As the turret is raised, pin 154 at the illustrated hole.152 disengage and,

after turret indexing and lowering, another hole 152 in the ring gear. The close toleranced complemental engagement between the pin 154 and the holes 152 accurately positions the turret after each indexing operation. As best seen in Figure 4 the top of pin 154 is slightly tapered whereby upon lowering of the turret if the lower, larger diameter portion of the pin is not accurately registered with the related hole 152, the tapered upper end of the pin rotates the turret slightly to proper indexed position whereat the pin 154 is received within the opening 152 as shown in Figure 4.

Attention is now directed to Figure 10 illustrating the detailed construction of the indexing mechanism 112. The ring gear of the turret is illustrated at 146. The rack 150, which engages the gear 146, is shown mounted in a bracket 162, which is secured to the table segment 34 and permits reversible linear movement of the rack 150. Spaced from the rack 150, a hydraulic actuating cylinder 164 having a reciprocal piston (not shown) is mounted on the segment 34. Hydraulic lines 166 and 168 communicate respectively with advance and return chambers (not shown) of the cylinder 164. A reciprocal piston rod 170 protrudes from one end of the cylinder 164 and is connected to the rack 150, by an adjustable connection 172. It will be noted that the limit switches LS5 and LS15 are so positioned relative to the indexing mechanism, that they are respectively actuated by the full advance and full return of the mechanism.

Referring now to Figure 5, wherein is illustrated the frame arm-clamping cylinder construction of arm. 18. It will be understood that the detailed construction of the arm 16 is not shown, inasmuch as it is similar both in construction and operation to that of the illustrated arm 18, except that arm 16 supports two clamping cylinders. The clamping assembly 25 is arm supported adjacent the column 22. It comprises a cylinder 174 and a piston 176 reciprocally mounted within the cylinder and dividing same into advance and return chambers 17 8 and 180, respectivel The lower end of the piston is fixedly secured to the die carrying plate 20, whichin turn is vertically slidable on the adjacent column 22 by means of the hushed hole within the plate shown at 182. The die plate carries the upper half of the die 24 in this figure illustrated in phantom at 184. Advance and return hydraulic lines (not shown) communicate respectively with the advance and return chambers 178 and 180, whereby the carried die half 184 is moved vertically into and out of engagement with the lower half of the die 24 in response to the actuation of the clamping piston.

It will be noted that the cylinder piston assembly is conventionally sealed and gasketed at 186 to prevent escape of the actuating hydraulic fluid.

The piece part delivery unit 100 is illustrated in detail in Figures 12 and 12A. Referring to said figures, it will be seen that the unit consists of a mounting plate 190 which carries at one end thereof the cylinder mounting bracket 192 and at the other end thereof a supporting bracket 194. Secured to one side of the bracket 192 is an air cylinder 102 which has a reciprocal piston (not shown) disposed therein. Connected to the piston is the piston rod and link 198 extending from one end of the cylinder 102 and through a complementary opening 197 in the bracket 192.

Spaced intermediate the brackets 192 and 194 are a pair of spaced parallel bars or ways 199, 199 which are connected at opposite ends to the respective brackets. A slide 200 having horizontally spaced holes 202, 202 extends between the bars, said holes slidably receiving the respective bars. Intermediate and below the ways or bars 199, adjustable connection is made between the slide 200 and the protruding end of the piston rod 198 as at 204.

Centrally of the slide 200 an upwardly extending lug 206 is presented with a hardened insert 208 secured thereto. Guide plates 210, 210 are disposed in a V relation the pin 154 reengages on opposite sides of the lug 206, said guide plates extending between and having their opposite ends adjustably connected to the brackets 192 and 194.

As best seen in Figure 12A, a heated piece part illustrated in phantom at 203 is delivered to the loading unit by means of the plate 201 appropriately arranged relative to a storage hopper and heating unit (not shown). With the part 200 cradled between the guide plates 210, 210, the air cylinder is actuated, urging the slide forward and bringing the insert 208 into contact with the end of the piece part. Thus the part is urged into place within the turret 12.

It will be noted that the storage hopper and heating unit are conventional devices Well known in the art. For this reason, said hopper and unit are not per se inventive, hence not shown. Suffice it to say that the piece part is heated to a desired working temperature, before delivery to the loading unit.

A lost motion limit switch actuating rod 212 is mounted adjacent and approximately parallel to the delivery unit 100. Mounting brackets 214, 214 loosely support the rod 212 to permit reciprocal movement relative thereto. One end of the rod 212 is connected to an actuating arm or lever 216 of a limit switch LS -i which is also mounted to plate 190. Stop collars 218, 218 are adjustably fixed to the actuating rod 212 at various desired points, said collars serving both to initiate and limit reciprocal movement of the arm 212. A lever 220 fixedly attached to the slide 200 depends therefrom to loosely embrace the rod 212. As the slide reciprocates on the ways 199, under the action hereinafter described, the arm 220 passes along the rod 212, and in the full advance or full return position of said slide strikes one of the collars 218 urging the rod 212 to move, thus tripping the switch LS4. The action of the limit switch LS-4 partially controls the advance and return of the loading unit by means of being electrically interlocked with valves 104 and 106 (Figure 2). Thus as the loading unit reaches full advance position, switch LS4 is tripped, closing valve 104 and opening valve 106. Valve now bleeds the trapped air from the advance chamber while valve 106 admits air to the return chamber, which in turn urges the return of the loading unit to neutral position. Return of the unit to neutral position again trips switch LS-4 setting up the electrical circuit for a new loading cycle, the operations of which will be explained in connection with the electrical circuit.

Attention is now directed to Figures 2, 11 and 11A for a particular description of the function and operation of the ejector mechanism 110. As noted above, the plate 108 is secured to the table segment 34. Spaced support brackets 230, 230 are fixedly secured to the plate 108. Intermediate the brackets 230 and connected thereto is a piece part guide 232. The cross sectional view of Figure llA illustrates the guide 232 as having a central portion or groove 234 of truncated V-shape and chain guide ledges 236 at each side of said central portion.

The top plate 238 of each bracket 230 is seen in Figure 11 to extend outboardly from the bracket, whereat is presented a sprocket shaft bore 240. A rotatable idler shaft 242, having sprockets 244, 244 mounted on opposite ends thereon, is disposed in one bore 240. A rotatable drive shaft 246 having sprockets 248 mounted thereon is disposed in the other bore 240. It will be noted that the sprockets 2'44 and 248 are arranged in alignment with the chain guide ledges 236.

A conventional gear box speed reducer 251 is seen in Figure 2 to be mounted on the plate 108 adjacent the drive shaft 246. An output shaft 250 extending from the gear box is conventionally coupled to the drive shaft 246, as at 252. Also mounted on the plate 108 is the fluid motor 254, which is conventionally coupled to the gear box input shaft 256, as at 258.

Chains 260, 260 interconnect aligned sprockets on the drive and idler shafts, said chains mounting the transversely aligned upwardly extending fingers 262, 262. Spaced rearwardly of the related fingers 262 a distance slightly greater than the length of a piece part, shown in phantom at 264 in Figure 11, are the bumper bars 266. Each bumper bar extends transversely of the guide 232 and has its opposite ends secured to aligned lengths of the chains 260.

Operation of the ejector unit is relatively simple, in that the chains and carried fingers and bumper bars move in a closed path about the sprockets 244 and 248 in response to action of the fluid motor 254. As a pair of fingers approach the turret, they embrace the body of the finished piece part and engage the formed flange thereof. Continued motion of the chains 260 urges the piece part from its frictionally held position in the turret and carries it along the groove 234. When the fingers reach the driving sprocket 248 they detach from the piece part and drop downwardly continuing to follow the path of the chain. This, of course, leaves the piece part resting in groove 234. The trailing bumper bar 266 then contacts the end of the piece part urging it from the ejector unit and into any suitable receptacle (not shown).

It will be noted that the fingers 262 actuate the limit switch LS-6 after each piece part extraction. The resulting operation will be explained in connection with the electrical diagram.

Attention is now directed to Figures 6 to 9, wherein is illustrated a typical forging station 26. It will be noted that all of the stations are substantially similar in both construction and operation, changes in individual stations being made only in piston areas and length of stroke to accommodate the individual requirements of the particular station.

Each forging station comprises a housing 270 carried by and secured to the table 4 in such a position that the axis of a therein formed cylinder 272, when extended, intersects the rotational axis of the turret 12. A replaceable sleeve 273 is disposed tightly within the cylinder 272. A piston rod 276 is disposed within the sleeve 273 and has threaded on one end thereof a piston 278 which is in ring sealing engagement with the internal surface of the sleeve 273 whereby the cylinder is divided into an advance chamber 280 and a return chamber 282. The opposite end of the piston rod 276 extends outwardly through the open end of the cylinder 272 Whereat it is connected to the punch mounting block 29. It will be remembered that the punch mounting block or device 29 is reciprocally gibbed to the table. It will also be noted that the piston rod is conventionally sealed and gasketed at the open end of the cylinder 272 as at 284, whereby escape of the hydraulic fluid employed is prevented.

A punch 286 is threadedly mounted in the insert 290, said insert being received within the block 29 and serving to accurately align the punch relative to the mating die 24. A retainer bolt 288 serves to fixedly lock the insert 290 in the block 29.

As noted above, the die 24 contistsv of upper and lower halves, the lower half being securely fixed to the table 4 and the upper half being carried by the related die plate-clamping piston assembly. In Figure 6 the die cavity 292 is shown to be composed of hardened steel inserts deposited Within the die 24. This is conventional practice whereby the cost of the die, both original and replacement, is reduced.

Considering Figure 6, it will be seen that the return line 64 enters the cylinder 272 at a point adjacent the forward end thereof from whence it communicates with a passage 296 to the return chamber 282.

Considering Figures 6 and 7, together, Figure 7 com pleting the sectional showing of Figure 6, it will be noted that the advance hydraulic line 60 enters a shut-off valve housing 294 adjacent the lower end thereof whereat it communicates with a vertical passage 298. The passage 298 extends upwardly and communicates with a 9 horizontal passage 300 which in turn communicates directly with the advance chamber 280. As best seen in Figure 7, another passage 302 interconnects the advance chamber 280 and the passage 300 through the one-way check valve 304. The purpose of the check valve will be hereinafter described.

Passage 300 presents a valve seat 306 at a point intermediate the passage 298 in the advance chamber 280, said seat complementally receiving a valve head 308. Connected to the head 308 is the stem 310 which extends outwardly from the housing 294 to make connection with the conventional diaphragm 70. The stem 310 is conventionally sealed by the packing 312 to prevent escape of hydraulic fluid. As hereinbefore noted, the diaphragm 70 will be actuated by the control valve 66 in response to the energization of limit switch LS-9 (Figure 2) when a piece part fails to appear at the particular die station. Actuation of diaphragm 70 urges the head 308 to seat itself on the seat 306, thus preventing high pressure hydraulic fluid from entering the particular station. A spring 313 returns the valve head to neutral position upon deactuation of the diaphragm 70.

Figures 8 and 9 show the construction of the high pressure fluid flow control means 314. It will be seen that the control 314 is disposed in the passage 298 below the valve seat 306. The control 314 consists of an adjustable bolt 316 and lock nut 318 arrangement. The bolt being threadably movable into the passage 298 whereby the cross sectional area of said passage may be reduced or enlarged as desired.

The eflect of the variable action of the control 314 is to meter the flow of high pressure hydraulic fluid to the advance chamber 280. Its advantage lies in the fact that independent flow control is available at each station whereby delicate adjustments may be made to insure simultaneous and concurrent advance of each punch to the work. The control 314 eliminates the possibility of one or more of the punches advancing into the associated die before the other punches. This concurrent punch action prevents a particular punch from engaging and remaining engaged with its associated die and piece part for unreasonably long periods of time which would result in excessive heating of the punch and chilling of the part with the attendant possibility of getting the punch stuck in the Work or in any event of decreased punch and die life.

In normal operation of the forging stations, hydraulic fluid is admitted to passages 298 and 300. The relatively high pressure of the fluid causes the one-way valve 304 to unseat, whereby high pressure fluid is delivered to the advance chamber. As soon as the tapered pin 279 is withdrawn from the line 300, the one-Way valve 304 reseats itself and hydraulic fluid is admitted to the advance chamber directly through the passage 300. After the piece part has been contacted and the work completed, pressure fluid is then directed to the return chamber 282 through the return line 64. Since valve 304 is seated, fluid in the advance chamber is permitted to escape only through line 300. As the piston 278 returns, the tapered pin 279 enters the passage 300 partially sealing same, thus a small amount of the hydraulic fluid is trapped within chamber 280 and can only escape by bleeding to the passage 300 around the edges of the tapered pin 279. This halts the rapid return of the piston 278 and prevents the piston from being slammed to full return position.

Attention is now directed to Figure 13, wherein hydraulic operation of the machine is diagrammatically illustrated. Automatic operation of my machine involves cooperation between several distinct pressure crcuits, and it should be noted, that various hydraulic fluid mediums could reasonably be used in the respective circuits other than those utilized in the preferred embodiment.

A high pressure circuit, indicated generally at 330, is

employed to operate the forging stations and clamping rams. In general, itcomp-rises a reservoir of hydraulic fluid 332 preferably water, a series of conventional deliv ery pumps 331 connected to the reservoir, an air ballasted accumulator 333 and an accumulator control arrangement 335, whereby a large volume of high pressure fluid is always available for delivery to the particular operated units.

In this connection, it should be noted that the accumulator and accumulator control arrangement is not per se part of the herein disclosed invention, hence will not he described in detail. For a complete description of the arrangement used, reference may be had to the patents to Robert I. Feuchter 2,294,396 and 2,294,397, issued September 1, 1942.

A hydraulic control circuit, indicated generally at 334, directly operates the turret raising motors 30, 30, the turret indexing mechanism 112 and the ejector unit 110, and also operates the master valves 337 and 339, which control high pressure flow to the clamp cylinders 25 and the master valves 341 and 343 which control high pressure flow to the forging stations 26.

A third circuit employing air as the fluid medium operates the loading mechanism and the diaphragm 70. It is believed the operating of the loading unit and the diaphragm and control valve has hereinbefore been clearly explained, hence the operation will not be repeated.

The control circuit 334 comprises a reservoir of hydraulic fluid 338, preferably oil, feeding a plurality of constant delivery pumps 340 arranged in parallel, each pump feeding different circuits. Associated with each pump 340 and related circuit is a conventional relief valve 342 permitting the delivered fluid to bypass the circuit and return to the reservoir 338. All circuits feed through their respective units to a common return mani-. fold 344 which also empties into reservoir 338.

The output of one of the pumps 340 is seen to feed through line 346 to the hydraulic control valve 348 which comprises a cylinder 350 and a flow control spool 352 movably disposed therein. As illustrated, the spool 352 is in the turret down position allowing the hydraulic fluid to escape to the return manifold 344. Upon energizing of solenoid J, the spool 352 is moved to the extreme right position against the compression of spring 354. In this position pressure fluid is directed through the valve 348 to the line 356 and thence to the motors 30. The motors 30 in turn raise the turret. Upon deenergizing of solenoid 1, spring 354 urges the spool to the extreme left position whereby the high pressure fluid is again directed to the return manifold and the turret is lowered by gravity. The hydraulic fluid in the motors 30, 30 is allowed to escape to the return manifold through the line 358.

Another pump 340 is seen to feed both the turret indexing mechanism 112 and the ejector unit 110. A line 360 carries the pressure fluid to the control valve 362 which also comprises a movable flow control spool 364 shown in neutral position. As solenoid G is energized, the spool 364 is moved to the extreme left position whereby the pump pressure is direct through line 366 to the return side of the indexing cylinder 112. Return of the indexing mechanism urges fluid trapped in the index advance chamber 368 to escape through lines 370 to line 372 which communicates with the control valve 374. As will be seen in connection with the electrical operation hereinafter described, solenoid I is energized simultaneously with solenoid G, thus the spool 376 of valves 374 is urged to the extreme right against the compression of spring 377. In this position, the line 378 to the return manifold is closed and communication is established between the line 372 and the line 380 which carries the pressure fluid to the ejector motor 254. Thus the ejector unit will operate simultaneously with the return of the index mechanism 112. Deenergizing of solenoid I and the return of spool 376 to neutral is 11 accomplished by action of the ejector fingers 262, momentarily opening switch LS-6, as will be more clearly hereinafter explained. Thus the ejector unit stops before the index mechanism reaches full return position. Upon stopping of the ejector unit, the pressure fluid in line 372 is directed to the return manifold 3 .4 via the line 378. Upon full return of the indexing mechanism 112, switch LS is opened and solenoid G is deenergized returning the spool 364 to the neutral position.

Energizing of solenoid H urges the spool 3/64 to move to the right, whereby pressure fluid is directed into line 370 and to the indexing advance chamber 368. This, of course, causes the indexing of the turret 12. With the spool in the extreme right position, fluid trapped within the index cylinder return chamber is permitted to escape through line 366, through valve 362, into line 372;, which carries it through valve 374 and to the return manifold 344 via line 378.

Control valves 38s) and 332 are fed with hydraulic fluid by the third pump 340 through lines 384 and 386, respectively. Said valves in turn control fluid flow to the hydraulic motors 388 and 390, which by mechanical interlock control the operations of the high pressure master valves 337, 339 and 341, 343.

Control valve 380 comprises a movable flow control spool 392 actuable in opposite directions by solenoids A and B. Energizing solenoid A urges the spool 392 to move from the neutral position shown to the extreme left, whereby pressure fluid is directed from line 334 through valve 380 into line 394 and to chamber 396 of the motor 388. An escape passage is provided from chamber 420 through lines 418 and 419 to the return manifold 344. The piston-piston rod assembly 393 of the motor 388 are urged to move upwardly causing arms 4% and 492, which are respectively fulcrummed to master valves 337 and 339 at points 404 and 406, to move clockwise about said fulcrum points. The action of arm 49% raises valve 408 from its seat which allows high pressure fluid from line 330 to be directed into line 410 and then to the advance chambers of the clamping cylinders urging the pistons downwardly and bringing the carried die halves into complementary engagement. Concurrently with the action of arm 4%, arm 492 is moved clockwise about its fulcrum 406 which raises valve 412, thus establishing an escape passage from the clamp cylinder return chamber through line 414 to the high pressure return manifold 416.

Energizing of solenoid B moves the spool 392 to the extreme right position, whereby pressure fluid is directed from line 384 through the valve 38% into line 418 and then to the chamber 420 of the motor 388. An escape passage is opened from chamber 3% through lines 394 and 419 to the return manifold 344. The piston rod assembly 398 is urged to move downwardly carrying arms 400 and 402 counterclockwise about their respective fulcrums 404 and 406. In response to this action, valves 422 and 424 are moved upwardly establishing an escape passage between the clamp cylinder advance chambers through line 410 and to the return manifold 416 and concurrently directing high pressure fluid from line 33% through line 414 and into the clamp cylinder return chambers whereby said clamps are urged upwardly and the carried die halves are separated.

In connection with the upward and downward movement of the clamps, it will be understood that two of the clamps have mounted thereon a lost motion limit switch actuating linkage 426, said linkage being schematically shown, however, only on one cylinder. The operation of the linkage is such that both the double throw limit switches LS21 and 2, LS2l(a) and 2(a), LS31 and 2 and LS3-1(a) and 2(a) will be thrown only at the extreme upward and downward position of the clamps. For example, at the extreme upward position of the related clamp, LS21 will be open and LS2l(a) 12 will be closed and LS3-1will be closed and LS31(a) will be open.

A movable flow control spool 428 of valve 382 is actuable in opposite directions by solenoids C and D. Upon actuation of solenoid C, the spool 42? is moved from the illustrated neutral position to the extreme left position. Pressure fluid from line 386 is then directed through the valve 382 into line 430 and thence to the chamber 432 of the motor 39%. Pressure fluid in chamher 432 causes the piston-piston rod assembly 434 to move upwardly carrying arms 436 and 438 clockwise about their respective fulcrum points 449 and 442. The action of the spool 428 also allows the fluid in chamber 444 to escape through lines 446 and 448 to the return manifold 344.

Clockwise movement of the arms 436 and 43S, respectively, raises the valves 450 and 452, valve 450 directing high pressure fluid into the advance manifold 69 and thence to the advance chambers of each forging station 26, valve 452 providing an escape passage from the return chambers of each station 26 through the manifold 62 and the line 454 and to the return manifold 416. Thus the punch at each station is urged forwardly to engage the associated die.

Energizing of solenoid D urges the spool 428 from the neutral position to the extreme right, thus directing pressure fluid from the line 386 to the chamber 444 of the motor 390 via the line 446. Said spool movement also establishes an escape passage from the chamber 432 through the line 430 and 448 to the return manifold 344. Pressure fluid in chamber 444 moves the pistonpiston rod assembly 434 downwardly which carries the arms 436 and 438 counterclockwise about their respective pivots 440 and 442. This action raises the valves 458 and 460 directing high pressure fluid to the line 454 through the return chambers of the respective stations via the manifold 62 and opens an escape passage from the advance chambers of the respective stations through the manifold 60 and to the return manifold 416. Thus the punches at each station are urged to the full return position.

The operation of the lost motion limit switch actuating arm 44 has been hereinbefore explained, but it should be noted that the arm and the limit switch assemblies are mounted at each station although shown schematically at only one station. It will also be noted that the switch LS11, LS1-1(a) is a double throw limit switch actuable only at the extreme positions of the associated station and that the switch LS8-1 is a normally open single throw switch, which is closed on the return stroke of the associated station supply before said station reaches the maximum return position.

Referring now to Figure 14, wherein is illustrated a preferred electrical control circuit for my novel machine. It will be seen and understood by those skilled in the art, that my control circuit provides for full automatic operation of the above described machine or, in the alternative, individual jogging operation of each operative unit of said machine. Both the full automatic operation and the jogging operation will be considered in that order.

A conventional 440 volt, 3 phase, single cycle, alternating current electrical supply provides power source for all electrical units. A control transformer TR is connected to two of the three phase lines and delivers to the control circuit volt, 60 cycle, single phase alternating current, the control circuit is fused at P to prevent overload and an emergency stop switch SW-3 is provided in series in the main line of the control circuit. It will also be seen that the solenoid circuits connect directly to the 440 volt supply, the solenoid circuits being fused against overload at L and M.

To better understand the automatic operation of the machine, it will be well to keep in mind the sequential and concurrent operational phases of the various mechanisms of the invention. First, it will be understood that the following broad sequence of actions occur;

(a) The clamp descends, engaging the mold,

(b) The punches are urged inwardly to form the metal and return to the neutral position,

() The clamps are raised,

(d) The turret is raised,

(e) The turret is indexed, and

(f) The turret is lowered to a new position.

Concurrently with the punchs in-punchs out operation, the loading mechanism loads the turret and returns, the index cylinder is returned to neutral position preparatory to the next indexing operation, and the stripper is operated to remove a completely finished piece part from the turret.

For automatic operation of the machine, the selector switch SW-l is first placed in the automatic position. The automatic start switch SW-2 is momentarily depressed thus closing a circuit through CR-l which is energized. CR-l closes the normally open relay CR-1(a) which holds the circuit through CR-1. CR-l also closes the normally open relays CR1(b), CR1(c), CR-1(d), CR1(e), CR-1(f), CR1(g) and CR-1(h).

The momentary contact at SW-Z also establishes a circuit through the closed portion of the double throw limit switch LS3-ll and 2 energizing CR3. CR3 closes normally open switch CR3(a) which holds the circuit through CR3. CR3 also closes normally open switches CR-3(b), CR3(c), and CR3( CR3 also opens normally closed switches CR3(d) and CR3(e) in the clamp up and turret up circuits, thus positively preventing machine malfunction in this respect. The closing of switches CR3( energizes solenoid A, which in turn permits actuation of the hydraulic clamp motor thereby bringing the clamps down.

As the clamps descend and the bottom closing the molds, segments LS3-1 and LS3-2 of the double throw limit switches are opened and the other segment of said double throw limit switches LS31(a) and 2(a) are closed. It will be noted that the circuit is held through CR-3 by the parallel lines through normally closed switches CR5(a) and CR7 (a). The closing of switches LS3-1(a) and 2(a) establishes a circuit through limit switches LS11 to 5, the now closed relay CR-3(h) and the normally closed relay CR5(c), thus energizing CR4. CR-4 closes normally open switches CR-4(a) energizing solenoid C, which in turn accommodates delivery of high pressure fluid to the forging stations, thereby urging the punches into engagement with the dies. CR4 also opens normally open switch CR4(b), thus positively preventing interference with the punch advance stroke until said stroke is completed. CR4 also opens normally closed switch CR4(c) in the index turret circuit.

As the punch at each station reaches its full advance position it opens the related limit switch LSl-l to 5 and closes the related and mechanically interlocked limit switch LS1-1(a) to 5(a). It will be noted that the parallel arrangement of the limit switches LSl-l to 5 maintains the circuit through CR-4 until all stations have reached the full advance position. At this point the circuit through CR4 is broken, CR4 is deenergized, switches LSl1(a) to 5(a) are closed and switch CR4(b) is returned to its normally closed position, thus establishing a circuit through CRS.

CRS immediately closes normally open switches CR5(b) whereby solenoid D is energized, which in turn accommodates delivery of high pressure fluid to the punch return chambers, thus returning the punches to the neutral position and closing limit switches LS1-1 to 5 and opening switches LS1-1(a) to 5(a). To positively prevent reenergizing of CR4 and the punch-in in circuit during punch return, CRS opens normally closed switch CRS (c) in said circuit. CRS also closes normally open switch CR-5(d) in the turret up circuit.

It will again be noted that the multiple parallel limit switches LS1-1(a) to 5(a) maintains the circuit through CR-S until all punches are returned to the full neutral position.

Considering now the operations concurrent with the punch action hereinbefore noted, it will be seen that the closing of switches LS3-1(a) and 2(a) by the clamps also establishes a circuit through LS-4, normally closed relay CR7 (a) energizing CR6. CR-6 closes normally open switch CR-6(a) energizing solenoid F which in turn causes a tube to be loaded in the turret by actuating the tube loading unit. CR6 also closes normally open switch CR-6(b) establishing a circuit through closed switch LS-15 and energizing CR8. CR-S closes normally open switch CR8(a) thereby holding the circuit through CR8. CRS also closes normally open switch CR8(c) thereby energizing solenoid G which causes the return of the index cylinder to the neutral position. The circuit through CR-B is broken by the opening of limit switch LS-lS by the index cylinder as it returns to neutral position.

CR6 in addition to establishing the circuit through CR8 also opens normally closed switch CR6(c) in the loading cylinder return circuit. As theloading operation is completed, the load cylinder reverses the mechanically interlocked limit switch LS-4 opening the circuit through CR6 and closing the circuit through CR-7 and CR-7A inasmuch as deenergizing of CR6 returns the switch CR-6(c) to its normally closed position. CR7 closes the normally open switch CR-7 (d) thus maintaining the circuit through CR7 and CR-7( a) until the limit switches LS3-1(a) and 2(a) are opened by the raising of the clamps. I

CR7 closes normally open switches CR7 (b), energizing solenoid E, whereby the loading cylinder is returned to the neutral position. CR7 also opens normally closed switch CR-7 (a). It will be noted that with CR-7(a) open, the circuit through CR-3 will be broken when the punch return stroke deenergizes CR-S, hence opening CR5(a). With CR3 deenergized, CR-3(a) is returned to normally open position. Deenergizing of CRS also opens CR3(b) which prevents a circuit being made through CR4, even though the limit switches LS1-1 to 5 are returned to closed position by the action of the punch return.

As noted above, CR-8 is energized by the action of CR6(b), the circuit being held through CR-8 by closing of switch CR-8(a). CR8 also closes normally open switch'CR-8(d) whereby a circuit is established through CR-10. CR10 closes normally open switch CR10(a) energizing solenoid I, which in turn causes the ejector unit to remove a finished piece part from the turret. After removal of the finished part, the ejector unit momentarily closes limit switch LS-6 establishing a circuit through CR9. CR9 closes normally open switch CR-9(a) thereby holding the circuit through CR9 until such time as CR8(d) is opened in response to the opening of the limit switch LS-15 by the index cylinder return. CR9 also opens normally closed switch CR-9(b) thereby deenergizing CR-ltl and stopping the stripper unit before the loading cylinder has completely returned.

Returning now to the sequential operation of the machine, it will be remembered that the opening of the circuit through CR3 is responsive to the energizing of CR-5, whereby CR-5(a) is opened. Therefore also responsive to the action of CRS is the closing of CRS (d) and the returning of CR-3(d) and CR3(e) to the normally closed positions thereby establishing a circuit through CR-11. It will be seen that this circuit cannot be established unless the series limit switches LS8-1 to 5 are closed by the return of the individual punches at the forging stations. Said limit switches LSS-l to 5 are in fact closed by the return of the punches at the associated stations at some point shortly before the punches reach the full return position. The result is that CR-S will still be energized when said limit switches are closed, hence the circuit will be established through CR11.

CR-11 closes normally open switch CR-11(a) thereby holding the circuit through CR-ll after CR-(d) has opened and until the mechanically interlocked double limit switches LS21 and LS2-2 are opened by the clamp returning to its fully raised position. CR-ll also closes normally open switches CR-11(b) which energizes solenoid B thereby causing the related hydraulic motors to raise the clamps. It will be remembered that CR7A once energized remain so until the clamps return to the fully raised position and open limit switches LS3-1 (a) and 2(a). Because CR-7A is energized, CR-7A(c), though normally open, is now closed, hence a circuit is established through normally closed CR3(e) and the now closed CR-5(e) whereby CR-12 is energized. CR-12 closes normally open switch CR12(a) thus establising a parallel holding circuit through CR-12 and around CR5(e) to maintain the circuit through CR12 when CR-5(e) opens in response to the deenergizing of CR5. CR-12 also closes normally open switches CR-12(b), whereby solenoid J is energized causing the turret to be raised. It will be noted that the above described circuit arrangement enables both the clamps and turrets to be raised substantially simultaneous.

CR-lZ also closes normally open switch CR-12(c) which maintains a circuit through CR-lZ around the open limit switches LS2-1(a) and 2(a).

When the clamp is returned to maximum raised position, limit switch LS3-1(a) and 2(a) are opened and switches LS3-1 and LS32 are closed preparatory to starting a new cycle. The opening of LS3-1(a) and 2(a) deenergizes all control relays from CR-4 to CR-lti and their related switches that may still be functioning. This leaves CR11 and CR12 still energized.

As the turret is raised to the maximum up position, the mechanically interlocked limit switches LSZ-l and 2 open and LS2-1(a) and 2(a) are closed. The open ing of LS2-1 and 2 deenergizes the circuit through CR-ll and the switches controlled thereby. The closing of the switches LS2-1(a) and 2(a) affords a parallel circuit path through CR-12 thus insuring that the turret will remain raised during the subsequent indexing operation. At this point in the cycle, CR-4 and CR8 have been deenergized, thus returning CR4(c) and CR-8(e) to the normally closed position. When the turret reaches the maximum up position, limit switch LS-7 is closed atfording a circuit through C1143. CR13 closes the normally open switch CR13( b) thereby holding the circuit through CR-l3. CR13 also closes the normally open switches CR-13(c) energizing solenoid H which causes the turret indexing mechanism to advance thereby indexing the turret.

CR-13 also closes normally open switch CR13(a) thus setting up the clamp cylinder delivery circuit for energizing upon the closing of LS-5 by the index cylinder as it reaches the maximum index stroke. Thus it will be seen that the open switch LS5 provides the proper time delay to permit indexing before the inauguration of the next machine cycle.

It should also be noted that switch LS-12 is normally closed in the clamp cylinder delivery circuit, but it will open if the stripper unit fails to remove a tube from the turret thus preventing a new cycle from originating upon the happening of that event.

Normally, however, LS12 is closed, hence upon the closing of LS-5 the index cylinder CR-3 is energized, which in turn creates a holding circuit through CR-3 (a) and the cycle is again started.

Limit switches LS9-1 to 5, as noted above, are positioned intermediate the turret and each die and are normally open when a tube appears in the related die. When a tube fails to appear in each die that particular 16 limit switch, for example LS9-1, would open and energize the associated solenoid, here solenoid 1. Energizing solenoid 1 permits the air pressure to actuate the diaphragm valve 70, as noted above, which in turn prevents the functioning of the particular station.

Jogging control of the circuit will be easily understood by those skilled in the art. To set up all jogging circuits, the selector switch SW1 is turned to the jog position which causes the circuit through CR-Z and CR-ZA thereby energizing same. CR-2 opens normally closed switches CR-2(a), CR2,(b), Cit-2(a), and CR2 (d) thereby preventing accidental energizing of any of the automatic circuits. CR-2 also closes normally open relays CR-2(e), CR2(;f), CR-2(g), CR-2(h), CR2(i), and CR-2(j) which respectively set up the clamp down, the punch in, the punch out, load, load return and index return circuits for manual control responsive to the depression of the related jog button.

CR-2A closes normally open switches CR-2A(b), CR-2A(c), CR-2A(d), and CR-2A(i), which respectively set up the stripper unit, clamp up, turret up and index turret circuits for manual control responsive to the depression of the related jog button. It will be noted, however, that the same jog button controls both the index return and stripping circuits inasmuch as the index and stripper mechanisms are operated by a single hydraulic circuit.

I claim:

1. in a machine of the class described, a piece part holder rotatable on an axis and movable axially along said axis to an indexing position and to another position, means for moving said holder to said positions, means responsive to indexing position of said holder for automatically rotatably indexing the latter, said holder having a plurality of part holding means, a plurality of workin means, each of said holding means being successively indexed with said working means in response to successive rotational indexing of the holder, means responsive to rotation of the holder to an indexed position thereof for moving the holder to said other position whereas parts carried by said holding means are indexed with related working means, die means responsive to movement of the holder to said other position thereof for automatically clamping said parts, means responsive to clamping work parts by said die means for automatically actuating said working means, and means responsive to movement of said holder to said other position thereof for automatically removing an associated part from a holding means which has passed all of said Working means.

2. In a machine of the class described, a piece part holder having a plurality of part holding means, said holder being rotatably indexable in increments about a rotational axis and being movable axially along said axis to an indexing position and to another position, a plurality of forging means, said holding means being successively indexed with said forging means by successive rotational indexing of said holder, means responsive to movement of the holder to said indexing position for automatically rotatably indexing the holder one increment, means responsive to rotation of the holder to an indexed position for automatically moving the holder to said other position thereof whereat the holding means are associated with related forging means, and means responsive to movement of said holder to said other position thereof for automatically actuating said forging means.

3. In a machine of the class described: a piece part holder rotatable on an axis; segmental table means arranged for carrying a plurality of work stations, each of said segmental table means being individually pivotable about said axis; a plurality of frame arms; clamping ram assemblies carried by said arms and means for individually pivoting; said arms about said axis for correlating the clamping ram assemblies with said work stations.

4. In a machine of the class described, a piece part holder having a plurality of part holding means, said holder being rotatably indexable in increments on a rotational axis and being movable along said axis to an indexing position and to another position, a plurality of working means and a stripping means with which said holding means are successively indexed, an hydraulic motor operatively connected to said holder in said indexing position thereof, said motor having an advance chamber to receive pressure fluid and having a return chamber from which such fluid is expelled upon indexing of said holder, said motor being automatically released from operative connection to said holder when the latter moves to said other position thereof, an hydraulic motor operatively connected to the stripper for actuation thereof, means connecting the last mentioned motor with the advance chamber for actuation by fluid expelled therefrom when the first mentioned motor is actuated to return position, and means for admitting pressure fluid to said return chamber when the holder is in said other position thereof.

5. In a machine of the class described, a frame, a workpiece carrying turret rotatably indexable on an axis and movable axially along said axis to an indexing position and to a working position, means for moving said turret to said positions, a ring gear on said turret, a rack movably carried by the frame and engageable with the ring gear only in said indexing position of the turret, motor means for advancing and returning said rack, means responsive to indexing position of the turret for actuating the motor means to advance the rack and thereby index the turret, means for working on a piece carried by the turret, means responsive to working position of the turret for actuating the motor means to return the rack, and means actuated by said motor means in returning the rack for stripping from the turret a workpiece which has been indexed past said working means.

6. In a machine of the class described: a piece part holder rotatable on an axis; table means comprising a plurality of segments individually pivotable on said axis for accommodating insertion of additional segments, each of said segments being arranged to carry one or more work stations; a plurality of frame arms, one for each table segment, means for individually pivoting said arms about said axis for maintaining alignment of said arms and said segments, clamping means carried by said arms and operatively associated with each of said stations.

7. In a machine of the class described, a workpiece carrying turret rotatably indexable on an axis and movable axially along said axis to an indexing position and to a working position, means for moving said turret to said positions, a ring gear on said turret, a rack having teeth engageable with the ring gear only in said indexing position of the turret, motor means for advancing the rack to index the turret when the latter is in said indexing position thereof and for returning the rack when said turret is in said working position thereof, means carried by the frame for working on a piece carried by the turret when the latter is in said working position thereof, said frame and turret having complementary means interengageable as the turret moves to said working position thereof for accurately indexing the piece with the working means.

8. In a machine of the class described, a turret rotatable on an axis and movable axially along said axis to an indexing position and to a working position, means for so moving the turret, a ring gear on said turret, a rack engageable with the ring gear only in said indexing position of the turret, an hydraulic motor operatively connected to the rack and having advance and return chambers, valve means for delivering pressure fluid to the advance chamber and for discharging pressure fluid from the return chamber to advance the rack and thereby index the turret when the latter is in said indexing position thereof, means for performing work on a workpiece carried by said turret, means for stripping workpieces from said turret after said workpieces have been indexed passed said work performing means, and hydraulic motor means for actuating said stripping means, said valve means being operable to deliver pressure fluid to said return chamber and to deliver pressure fluid from said advance chamber to said last mentioned motor means for actuation of said stripping means in response to return movement of the rack when the turret is in said working position thereof.

9. In an automatically operated piece part working machine: piece part holding means; means for rotating said holding means in one plane; means for moving said holding means into another plane; means for intermittently indexing said holding means through a plurality of forging stations when said holding means are in said other plane; and means at each station to progressively work on piece parts when the holding means are in said one plane.

References Cited in the file of this patent UNITED STATES PATENTS 57,873 Crosby Sept. 11, 1866 559,526 Heermans May 5, 1896 596,830 Rodgers Jan. 4, 1898 685,465 Boyd Oct. 29, 1901 825,487 Saunders July 10, 1906 946,584 Smith Jan. 18, 1910 1,480,142 Bell Jan. 8, 1924 1,592,060 Wilcox July 13, 1926 1,743,564 Nagel Jan. 14, 1930 1,802,053 Halborg Apr. 21, 1931 1,939,038 Bower et al Dec. 12, 1933 1,975,005 Kingsbury et a1. Sept. 25, 1934 2,021,584 Wickman Nov. 19, 1935 2,165,912 Whitman July 11, 1939 2,202,017 Stocking May 28, 1940 2,227,796 Quillen Jan. 7, 1941 2,238,921 Waldsmith Apr. 22, 1941 2,249,964 Lindler July 22, 1941 2,251,948 Oberhoffken et al Aug. 12, 1941 2,272,720 Mariotte Feb. 10, 1942 2,284,575 Johnson May 26, 1942 2,309,998 Tucker Feb. 2, 1943 2,325,348 Tucker July 27, 1943 2,341,602 Dewey Feb. 15, 1944 2,358,389 Ewart Sept. 19, 1944 2,408,379 Day Oct. 1, 1946 2,429,938 Mansfield Oct. 28, 1947 2,449,365 Bober et a1 Sept. 14, 1948 2,513,710 Brauchler July 4, 1950 2,575,504 Wright Nov. 20, 1951 2,606,359 Stadthaus Aug. 12, 1952 2,647,421 Criley Aug. 4, 1953 2,682,186 Riemenschneider June 29, 1954 2,729,879 Sampson Jan. 10, 1956 2,729,943 Clarke et a1 Jan. 10, 1956 2,732,738 Krause Jan. 31, 1956 2,755,839 Garrock et a1. July 24, 1956 2,759,202 Marsden Aug. 21, 1956 FOREIGN PATENTS 41,732 Sweden Aug. 26, 1915 940,661 France Dec. 20, 1948 UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION Patent No., 2,891,431 June 23, 1959 Robert K.. Sedgwick It is hereb certified that error appears in the -printed specification of the above numbered patent requiring correction and that the said Letters Patent should read as corrected below.

Column 1, line 44, for "came" read same 3 column 4, lines and 26, for "outwardly read outboardl column '7, line 8, for "part ZOO read me part 203 column 8, line 53, for "threadedly" read threadeabl line 58, for "contists" read consists 0011111511 9, Tl, for "pressure crcuits" read hydraulic circuits line 72 for "hydraulic read pressure column 16, line '73, for "arms and read arms; and ===g line '74, for "pivoting; said" read as pivoting said Signed and sealed this 26th day of January 1960,

(SEAL) Attest: KARL Ho AXLINE ROBERT C. WATSON Commissioner of Patents Attesting Officer 

